Roll that can be bent for a web-like material

ABSTRACT

A roll that can be bent for a web-like material, which roll comprises a continuous tubular roll mantle ( 11 ) of composite material as well as axle journals ( 12 ) connected to each end of the roll mantle ( 11 ). The axle journals ( 12 ) are attached by means of at least one mechanism ( 30 ), by whose means the axle journals ( 12 ) and thereby the roll mantle ( 11 ) are bent into an arc form, and a regulation device ( 40 ) by whose means the angular position of the roll arc can be regulated.

FIELD OF THE INVENTION

The present invention relates to a roll, and in particular, to a rollfor a web like material.

BACKGROUND OF THE INVENTION

Most commonly, rolls that can be bent have been formed so that they havea continuous axle and a roll mantle composed of a number of parts fittedon the axle. The roll can be curved in the desired shape by shifting theoutermost journalling points of the roll mantle in the radial direction,in which case the mantle forms an arc or a broken line. The parts of themantle have as a rule, been mounted on the axle each of them separately,in which case the arrangement comprises a number of bearings. Theconventional solutions often involve problems, which include, amongother things, bearing problems in the roll and heat peaks produced bythe bearings in the paper web. A roll mantle composed of a number ofparts may also form a considerable problem, because the gaps between theparts may mark the paper web and because the shape of the arc of theroll is not optimal, but the shape line of the roll is shaped as abroken line. Further, owing to the metallic roll mantle, problems ofcorrosion may arise.

The roll described in the applicant's FI Utility Model No. 2788comprises a non-revolving roll axle and a roll mantle mounted on theaxle revolving by means of bearings. The roll mantle is a continuoustubular mantle, and the roll axle consists of three parts linked witheach other. The inner ends of the two end parts of the roll axle, whichare hollow in the interior, extend a certain distance into the interiorof the hollow tubular middle part of the axle. In the end areas of theroll, support sleeves have been fitted, onto which sleeves the rollmantle itself has been mounted. The roll mantle has been mounted on eachof the end parts of the axle by the intermediate of said support sleevesby means of two bearings placed at an axial distance from one another.The end parts of the axle have been connected with the middle part ofthe axle by means of articulated members so that the end parts of theaxle can be inclined in relation to the middle part of the axle. Theinclining takes place so that the end parts of the axle move in relationto the middle part of the axle in the radial direction. The roll bendingmechanism comprises a cam member which forms a lever with two arms andwhich has been mounted pivotally on the wall of the tubular end part.The inner end of the cam member extends through the wall of said tubularend part to outside the end part and is supported against the inner faceof the middle part. In the interior of the tubular end part, an axiallydisplaceable regulation rod has been fitted, whose inner end issupported against the cam member. When the cam member is shifted in theaxial direction, the cam member can be pivoted so that it is supportedwith a greater force against the inner face of the middle part of theaxle while, at the same time, increasing the distance between the endpart and the middle part of the axle at the side of the cam member, inwhich case the axle is bent. The roll mantle can be made of steel or ofa composite material.

The solution described in said FI Utility Model No. 2788 is in itselfoperative, but it is relatively complicated and expensive.

The roll described in the applicant's FI Patent Application No. 970379is composed of two end parts and of a middle part. In this solution, theroll has no separate axle with a mantle revolving on said axle, but themiddle part also operates as the axle of the roll, which is mounted onits support members by means of end bearings. The extensions of themiddle part which operates as the axle have diameters substantiallysmaller than the diameter of the middle part, and their size correspondsto the diameter of an ordinary non-revolving axle. The end parts of theroll are tubular pieces, and they have been mounted directly onextensions of the middle part so that, at the inner ends of the endparts, articulation means have been fitted in the interior of thetubular end parts. The tubular end parts have been supported in theaxial direction, in the area of their outer ends, by means of bearings,which have been fitted on support parts separate from the revolvingparts. The support parts comprise sleeve-like pieces, whose innerdiameter is larger that the diameter of the extension of the middlepart, so that the positions of the bearings can be regulated radially.When the positions of the bearings of the tubular end parts areregulated, it is possible to regulate both the extent of curve form ofthe roll and the direction of the curve form. As the material of themantle of this roll, it is also possible to use a composite material.

In said FI Patent Application No. 970379, an axle is used that extendsthrough the roll mantle, and the whole of the construction of the rollis relatively complex, so that the cost of the roll becomes high.

In the FI Patent Application No. 951288, a roll is described that isprovided with a continuous roll mantle or with a roll mantle composed ofa number of parts. The material of the roll mantle is reinforced plasticor a similar composite construction. The roll is provided with acontinuous support axle extending across the whole roll mantle, whichaxle is not rotated and which is supported in its place. In the middleportion of the support axle there is a thicker portion, on which themiddle bearings of the roll have been mounted. Said bearings aresupported on annular fitting pieces, by whose means the outer race ofthe bearing is supported on the roll mantle. At the ends of the roll,sleeves have been installed so that the sleeves extend a certaindistance into the interior of the roll mantle and a certain distance tooutside the roll mantle. The ends of the roll mantle have beenjournalled on said sleeves. Onto the sleeves, in the portion outside theroll mantle, regulation screws have been mounted, by whose means thesleeve can be diverted from the centre line formed by the support axle.When the sleeves are diverted from the centre line formed by the supportaxle, at the same time the centres of the outermost bearings of the rollare diverted from said centre line, in which case the roll mantle isbent, but the support axle remains straight all the time.

In said FI Patent Application No. 951288, a continuous support axle isused which extends through the whole roll mantle and in whose middlepart there is a thicker portion. Thus, the roll becomes relativelyexpensive and heavy. Further, the roll has bearings also in the middleportion of the roll at the thicker portion of the support axle. Thesebearings fitted in the middle part of the roll cause said problems ofheat in the roll mantle, and attempts have been made to reduce saidproblems of heat by means of annular fitting pieces installed betweenthe outer races of the bearings and the inner face of the roll mantle.

In the EP Patent Application No. 363,887, a roll made of a compositematerial has been described. The invention of said EP patent applicationconcerns the structures and materials of different surface layers of theroll mantle. FIG. 4 illustrates a revolving roll manufactured inaccordance with the invention and meant for very high speeds, which rollis provided with a roll mantle of a composite material and with axlejournals at the ends of the roll mantle. The axle journals are connectedwith the roll mantle by means of end flanges. Said EP patent applicationis expressly concerned with the material structure of the roll mantle,the object being to manufacture a roll of sufficient surface hardness,low weight, and high dimensional precision. The application does notmention bending of the roll.

Owing to its numerous advantageous properties, a composite roll ishighly interesting. The roll solutions mentioned above, in which a rollmantle made of a composite material can also be employed, are, however,clumsy and expensive. Owing to the favourable material properties of acomposite roll, such as modulus of elasticity and density, a compositeroll can be dimensioned so that it can be bent to the desired curve formwith a reasonable torque and that it operates either at a speed belowthe critical speed, i.e. below the lowest resonance frequency, orbetween resonance frequencies. If a steel roll is supposed to be bent toa required curve form without increasing the strains excessively, theroll diameter must be very small. In such a case, one or severalcritical speeds of the roll must be surpassed unavoidably.

With a steel roll, the bending torque required by the bending is alsoconsiderably higher than with a composite roll, in which case thebearing forces at a steel roll are also considerably higher than with acomposite roll.

OBJECTS AND SUMMARY OF THE INVENTION

The solution in accordance with the present invention constitutes asubstantial improvement over the prior-art rolls that can be bent.

In the roll in accordance with the present invention, there is acontinuous tubular roll mantle of a composite material. At both ends ofthe roll mantle there are axle journals, by whose means the roll isattached to the frame of the machine. Thus, the roll has no axle passingthrough the roll at all. As compared with traditional spreader rolls,the construction of the roll in accordance with the present invention isclearly simpler, and its need of maintenance is little. The simpleconstruction makes the manufacture of the roll easy and of low cost.Also, the simple construction facilitates servicing of the roll.

BRIEF DESCRIPTION OF THE DRAWINGS

In the following, the invention will be described with reference to thefigures in the accompanying drawings, the invention being however, notsupposed to be confined to the details of said illustrations alone.

FIG. 1 is a schematic illustration of principle, in which a continuoustubular roll mantle is be means of a torque applied to both ends of theroll mantle.

FIG. 2 is a schematic illustration of an embodiment of the roll inaccordance with the invention in which the bearings are fitted in theinterior of the roll mantle and in which the bending mechanism is ascrew member.

FIG. 3 shows a variation of the embodiment shown in FIG. 2.

FIG. 4 shows a second variation of the embodiment shown in FIG. 2.

FIG. 5 shows a third variation of the embodiment shown in FIG. 2.

FIG. 6 shows a fourth variation of the embodiment shown in FIG. 2.

FIG. 7 is a schematic illustration of an embodiment of the roll inaccordance with the invention in which the bearings are fitted outsidethe roll mantle and the bending mechanism is a screw member.

FIG. 8 shows a variation of the embodiment shown in FIG. 7.

FIG. 9 shows a second variation of the embodiment shown in FIG. 7.

FIG. 10 is a schematic illustration of an embodiment of the roll inaccordance with the invention, in which the bearings are fitted outsidethe roll mantle and the bending of the roll is carried out in twoplanes.

FIG. 11 shows a variation of the embodiment shown in FIG. 10.

FIG. 12 shows a second variation of the embodiment shown in FIG. 10.

FIG. 13 shows a third variation of the embodiment shown in FIG. 10.

FIG. 14 is a schematic illustration of an embodiment of the roll inaccordance with the invention, in which the bearings are fitted outsidethe roll mantle and the bending of the roll is carried out by means of adisk attached to the axle journal and by means of hydraulic loadingelements acting upon said disk.

FIG. 15 is a schematic illustration of an embodiment of the roll inaccordance with the invention in which glide bearings are employed inthe interior of the roll mantle and in which the bending mechanism basedon hydraulics is connected with the glide bearings.

DETAILED DESCRIPTION OF THE INVENTION

FIG. 1 is an illustration of principle, in which the roll mantle 11 isbent by means of torques M₁, M₂ applied to both ends of the roll mantle11. The magnitude of the torque M₁ can be different from the magnitudeof the torque M₂, in which connection the running of the web proceedingon the roll mantle 11 can be controlled in the axial direction of theroll.

FIG. 2 shows an embodiment of the roll in accordance with the invention.In the figure, one end area of the roll is illustrated. The rollconsists of a continuous tubular roll mantle 11 of a composite material,which mantle has been fitted to revolve on the axle journals 12. In theend areas of the roll mantle, the first support sleeves 13 have beenfitted, on which sleeves the roll mantle 11 itself has again beenmounted. The roll mantle 11 has been mounted on axle journals 12 by theintermediate of said first support sleeves 13 by means of bearings14,15. The bearings 14,15 have been installed at a distance from oneanother in the axial X—X direction of the roll, and, thus, the bearingsform a pair of bearings.

In FIG. 2, the axle journals 12 consist of three parts 12 a, 12 b, 12 c,all of which have different diameters. The inner part 12 a, whichextends into the interior of the end area of the roll mantle 11, has thelargest diameter D₁, the following middle part 12 b, which is directedoutwards from the end of the roll mantle 11, has a slightly smallerdiameter D₂, and the outer part 12 c, which follows after the middlepart 12 b, has again a somewhat smaller diameter D₃ than the middle part12 b. The axle journals 12 can, of course, be physically composed of thesame piece, in which case said parts 12 a, 12 b, 12 c have been formed,for example, by turning on a lathe. In the middle area of the middlepart 12 b of the axle journal 12, there is a projection 16, whichextends around the circumference of the axle journal and which forms anarticulation member. Onto the outer part 12 c of the axle journal andpartly onto the middle part 12 b, a second support sleeve 17 has beenfitted. This second support sleeve 17 extends beyond the projection 16provided on the middle part 12 b of the axle journal 12, and the innerdiameter of the second support sleeve 17 is substantially equal to theouter diameter of the projection 16. The second support sleeve 17 hasbeen fixed to the frame R of the machine by means of two fasteningmembers 18, 19. The first fastening member 18 is placed at theprojection 16, and the second fastening member 19 is placed at adistance from the outer end of the outer part 12 c of the axle journal12 and of the second support sleeve 17.

In FIG. 2, bending of the roll into curve form takes place by means of abending mechanism 30 acting upon the outer end of the outerpart 12 c ofthe axle journal 12. In this embodiment, the bending mechanism 30consists of a screw member 30 extending through the end of the secondsupport sleeve 17 and through the outer end of the outer part 12 c ofthe axle journal 12. The screw member 30 is provided with an outerthreading extending substantially through the second support sleeve 17,and the bore which extends through the outer part 12 c of the axlejournal 12 and which receives the screw member 30 is provided with acorresponding inner threading. Further, movement of the screw member 30in the direction of its own longitudinal axis is prevented by means offastening members 31,32 supported against the outer face of the supportsleeve 17 and attached to the screw member 30, for example, by means ofcotter pins. When the screw member 30 is rotated, the axle journal 12 isbent, and the articulation member 16 permits axial shifting of the axlejournal 12 in relation to the second support sleeve 17. When the axlejournals 12 at both ends of the roll mantle 11 are bent, the roll mantle11 is also bent to the desired curve form.

In FIG. 2, by means of the regulation device 40, the second supportsleeve 17 can be rotated in the direction of its circumference. When thesecond support sleeve 17 is rotated in the direction of thecircumference, the screw member 30 and so also the axle journal 12 arerotated correspondingly. Thus, by means of the screw member 30, thedesired curve form is regulated for the roll mantle 11, and by means ofthe regulation device 40 the direction of the curve form of the rollmantle 11 is regulated in the direction of the circumference of the rollmantle 11. The second support sleeve 17 has been mounted in the first 18and the second 19 fastening member so that it cannot be rotated inrelation to the fastening members 18,19 in any other way except by theeffect of the regulation device 40. This is why the axle journal 12cannot be rotated in relation to the fastening members 18,19 either,except by the effect of the regulation device 40. The first fasteningmember 18 is provided with a first bearing member 20, which permitsrotation and a slight axial movement of the second support sleeve 17.Also the second fastening member 19 is provided with a correspondingsecond bearing member 21, which permits a slight axial movement of thesecond support sleeve 17. This second bearing member 21 is locked withthe support sleeve 17 so that the support sleeve 17 cannot be rotated inrelation to the second bearing member 21 in the direction of thecircumference. Further, the second bearing member 21 is coupled by meansof an intermediate member 22 with the regulation device 40. Thus, by theintermediate of the intermediate member 22 and the second bearing member21, the regulation device 40 acts upon the second support sleeve 17, inwhich connection the second support sleeve 17 revolves in the directionof the circumference by the effect of the regulation device 40.

In the following, the embodiments shown in FIGS. 3 through 14 will bedescribed in the respects only in which they differ from the embodimentshown in FIG. 2. In FIGS. 3 . . . 14, the same reference numerals willbe used for corresponding parts as have been used in FIG. 2.

FIG. 3 shows an embodiment in which the screw member 30 that bends theroll mantle into a curve form is placed between the first fasteningmember 18 and the end of the roll mantle 11, and not after the secondfastening member 19 as is shown in the embodiment of FIG. 2. The parts12 b and 12 c of the axle journal 12 change positions here, and thearticulation point 16 is placed at the second fastening member 19.

FIG. 4 shows an embodiment which differs from the embodiment of FIG. 2in respect of the fastening members 18,19. In the embodiment of FIG. 2,two fully separate fastening members 18,19 have been used, by whosemeans the second support sleeve 17 fitted on the axle journals 12 hasbeen attached to the frame R of the machine. In the embodiment shown inFIG. 4, a fastening flange construction is used in which there are twofastening members 18,19, which have a common lower part 90, which isattached to the frame R of the machine. Thus, the second support sleeve17 is still attached to the flange construction by means of twofastening points, which flange is also possible to think that the topportion of the fastening flange construction is made of one piece.

FIG. 5 shows an embodiment which differs from the embodiment shown inFIG. 2 in respect of the roll bending mechanism. In this embodiment, theroll bending mechanism consists of a screw member 60 parallel to theaxis X—X of the roll, provided with an outer threading, and placed atthe outer end of the second support sleeve 17. The screw member 60 hasbeen fitted in a fastening member 61, which is fixed to the inner faceof the second support sleeve 17 at its outer end and which is providedwith a bore with an inside threading that receives the screw member 60and that is parallel to the axis X—X of the roll. The inner end of thescrew member 60 is placed against the end face of a first wedge member70. The first wedge member 70 moves substantially parallel to the axisX—X of the roll on the inner face of the second support sleeve 17 by theeffect of the screw member 60, but it has been locked against the innerface of the second support sleeve 17 to prevent radial movement. Thewedge face of this first wedge member 70 is again placed against thewedge face of the wedge member 71 attached to the outer part 12 c of oneof the axle journals 12. When the first wedge member 70 is displaced bymeans of the screw member 60 to the left in the figure onto the secondwedge member 71, the axle journal 12 is bent, and so also the rollmantle 11 is bent.

FIG. 6 shows an embodiment which differs from the embodiments shown inFIGS. 2 through 5 in respect of the bending mechanism. As the bendingmechanism 100, a hydraulic or pneumatic cylinder or a stepping motor isused. The rod 101 of the cylinder or of the stepping motor has beenattached to an extension 12 d provided on the axle journal 12, and thecylinder or the motor has been attached to the second support sleeve 17.Thus, vertical movement of the rod 101 produces bending of the axlejournal 12.

FIG. 7 is a schematic illustration of an embodiment of the roll inaccordance with the invention, in which embodiment it is a difference ascompared with the embodiments shown in FIGS. 2 through 6 that thebearings of rotation of the roll are now placed outside the roll mantle11. In this embodiment, the axle journal 12 has been attached to the endmember 52 of the roll, which end member is fixed to the roll mantle 11,in which case the axle journal 12 revolves along with the roll mantle11. On the other hand, the axle journal 12 has been mounted revolving ona first support sleeve 50 by means of bearings 14,15. Here the axlejournal 12 is of substantially uniform thickness at least in respect ofits portion between said bearings 14,15. The first support sleeve 50 issurrounded by a second support sleeve 51, which has been attached to theframe R of the machine by means of fastening members 18,19, which areplaced at said bearings 14,15 in the direction of the axis X—X of theroll. At the end of the second support sleeve 51 placed next to the endmember 52, there is a thicker portion 51 a which extends across thefirst fastening member 18 in the direction of the axis X—X of the roll.At the thicker portion 51 a, the inner diameter of the second supportsleeve 51 is smaller than the inner diameter of the extension part 51 bfollowing after the thicker portion 51 a. Thus, between the firstsupport sleeve 50 and the extension part 51 b of the second supportsleeve 51, an empty space 53 remains, in which the outer end of thefirst support sleeve 50 can move in the radial direction. The thickerportion 51 a of the second support sleeve 51 forms an articulationmember of the first support sleeve 50, on whose support a littlemovement between the first support sleeve 50 and the second supportsleeve 51 in the direction of the axis X—X of the roll is possible.

In the embodiment shown in FIG. 7, the bending mechanism 80 alsocomprises a screw member 80 installed outside the second fasteningmember 19, which screw member extends both through the first supportsleeve 50 and through the second support sleeve 51. On the contrary, thescrew member 80 does not extend through the axle journal 12, whichterminates at the second support bearing 15 before the screw member 80.The screw member 80 is provided with an outer threading substantially inthe portions that pass through the first 50 and the second 51 supportsleeves. Movement of the screw member 80 in the direction of its ownlongitudinal axis in relation to the first support sleeve 50 isprevented by means of first fastening members 81,82 resting against theinner face of the first support sleeve 50 and attached to the screwmember 80, for example, by means of cotter pins. Further, to the outerface of the second support sleeve 51, second fastening members 83, 84have been attached, which are provided with bores with inside threadingsthat receive the screw member 80.

In FIG. 7, bending of the axle journal 12 of the roll is produced sothat the outer end of the first support sleeve 50 is displaced by meansof the screw member 80 in relation to the second support sleeve 51. Insuch a connection, the centre point of the second outer bearing 15 isdisplaced in relation to the central axis X—X of the roll, in which casethe axle journal 12 is bent, and the roll mantle 11 is also bent.

FIG. 8 shows an embodiment which differs from the embodiment shown inFIG. 7 in respect of the roll bending mechanism. In this embodiment, abending mechanism as described in the embodiment shown in FIG. 5 isused. Here the screw member 60 has been fitted in a fastening member 61,which has been attached to the inner face of the second support sleeve51 at its outer end and which is provided with an inside threading thatreceives the screw member 60. In order that the fastening member 61could be fitted on the inner face of the second support sleeve 51, thefirst support sleeve 50 is slightly shorter than the second supportsleeve 51. Here the second wedge member 71 has been attached to theouter face of the first support sleeve 50, in which case, beingcontrolled by the screw member 60, the wedge members 70,71 bend thefirst support sleeve 50.

FIG. 9 shows an embodiment which differs from the embodiments shown inFIGS. 7 and 8 in respect of the roll bending mechanism. Herein ahydraulic or pneumatic cylinder or a stepping motor is used as thebending mechanism 100. The rod 101 of the cylinder or stepping motor hasbeen attached to the first support sleeve, and the cylinder or steppingmotor has been attached to the second support sleeve. Thus, verticalmovement of the rod 101 produces bending of the axle journal 12.

FIG. 10 shows an embodiment of the present invention, in which thebending takes place by means of two bending means 120,130 in two planesperpendicular to one another. The bending means 120,130 have beenattached from one end to a substantially L-section support beam 110,which has again been attached to the frame R of the machine. On theother hand, the opposite ends of the bending means 120,130 have beenattached to a flange 113 that surrounds the second bearing 15. The firstbending device 120 displaces the axle journal 12 in the vertical planeY, and the second bending device 130 displaces the axle journal 12 inthe horizontal plane X. By means of this arrangement, the desired curveform of the roll can be regulated, e.g., by means of the first bendingdevice 120, and the desired angular position of the curve form of theroll can be regulated by means of the second bending device 130.

The bending means 120,130 shown in FIG. 10 consist of a nut member123,133 provided with inside threading, a first pin 121,131, which isfixed to a flange 113 and which is provided with an outside threading,being fitted to one end of said nut member, an a second pin 122,132,which is fixed to a sledge 124,134 moving on the beam 110 and which isprovided with an outside threading, being fitted to the opposite end ofsaid nut member 123,133. When the nut member 123,133 is rotated, theaxle journal 12 and, thereby, the roll mantle 11 can be bent in theX-Y-planes. By means of this arrangement, it is possible to regulateboth the curve form of the roll mantle 11 and the angular position ofsaid curve form. The sledge 124, which is fitted on the horizontal partof the beam 10, can move in the X-plane on support of the wheels 125,but it has been locked in respect of the beam 110 against movement inthe Y-plane. In a corresponding way, the sledge 134 fitted on thevertical part of the beam 110 can move in the Y-plane on support of thewheels 135, but it has been locked in respect of the beam 110 againstmovement taking place in the X-plane. The wheels 125,135 of the sledges124,134 revolve on guide rails or equivalent that have been formed onthe beam 110. The wheel arrangement 125,135 is just one example of amode in which the mounting of the sledges 124,134 on the beam 110 can beaccomplished so that movement of the sledge 124 in the direction X andmovement of the sledge 134 in the direction Y are permitted. In stead ofa nut-pin solution, herein it is also possible to employ, for example, ahydraulic or pneumatic cylinder or a stepping motor.

FIG. 11 shows a variation of the embodiment shown in FIG. 10, in whichthe journalling and bending of the axle journal 12 are carried out bymeans of at least one magnetic bearing. At least one of the bearings14,15 is a magnetic bearing 15, by whose means the axle journal 12 ofthe roll and, thereby, the roll mantle 11 can be bent. When the magneticflux in the magnets 250 of the magnetic bearing 15 and, thereby, theforce applied by the magnets 250 to the axle journal 12 are regulated,the axle journal 12 can be displaced eccentrically in relation to thehousing. Thus, the magnetic bearing 15 permits bending of the roll axle12 and, thus, also of the roll mantle 11 to the desired curve form inthe X-Y-planes and regulating of the angular position of the arc of theroll mantle 11 formed by bending to the desired position. Of course bothbearings 14,15 can also be magnetic bearings.

FIG. 12 shows a second variation of the embodiment shown in FIG. 10, inwhich the bending of the axle journal 12 and the angular position of thebending are regulated by means of a magnet 260. The flange 19 a thatsurrounds the second bearing 15 and the base part 19 b of the flange 19a, which is attached to the frame R of the machine, communicate witheach other by means of the magnet 260. The magnet 260 consists of anumber of sector-shaped parts, and the magnetic flux of each sector canbe regulated separately. By means of such an arrangement, the axlejournal 12 can be bent in the desired way in the X-Y-planes.

FIG. 13 shows a third variation of the embodiment shown in FIG. 10, inwhich the bending of the axle journal 12 is carried out by means of anut member 153, and the angular position of the bending is regulated bymeans of a rack-gearwheel device 160, 150. The flange 113 whichsurrounds the second bearing 15 has been attached to the gearwheeldevice 150 by means of the nut member 153. The nut member 153, providedwith an inside threading, is similar to the nut members 123,133 shown inFIG. 11, and to one of its ends a pin 151 projecting from the bearingflange 113 and provided with outside threading has been fitted, and toits opposite end a pin 152 projecting from the gearwheel device 150 andprovided with outside threading has been fitted. The gearwheel device150 comprises a gearwheel 154 mounted on the gearwheel device 150 bymeans of its shaft 155. The shaft 155 of the gearwheel 154 projects fromthe gearwheel device 150, and the projecting portion is preferably ofquadrangular section, in which case it can be rotated, for example, bymeans of a lever tool suitable for the purpose. The rack device 160comprises a rack 161 substantially shaped as an arc of a circle, alongwhich the gearwheel 154 runs. The rack device 160 further comprises aguide part 162, which glides in the guide groove 156 of the gearwheeldevice 150. The rack device 160 is attached to the beam 140, which isagain attached to the frame R of the machine. When the nut device 153 isrotated, the distance of the central axis X—X of the axle journal fromthe rack 161 can be regulated, in which way the axle journal 12 and,thereby, the roll mantle 11 can be bent. On the other hand, by means ofthe gearwheel 154 of the gearwheel device 150 it is possible to regulatethe angular position of the curve form of the roll mantle 11. Thegearwheel device 150 can be locked in the desired angular position onthe rack 161 by means of a screw locking device 157, which tightens thesledge 150 against the rack 161.

FIG. 14 shows an embodiment in accordance with the invention, in whichthe bending of the axle journal 12 is carried out by means of a diskmember 180 attached to the axle journal 12. The fastening flangeconstruction 170 attached to the frame R of the machine consists of twovertical walls of substantially rectangular shape placed at an axialdistance from one another, i.e. a front wall 171 and a rear wall 172.The bottom edge and the top edge of the front wall 171 and of the rearwall 172 have been interconnected by means of a substantiallyrectangular horizontal bottom wall 173 and top wall 174. Similarly, theside edges of the front wall 171 and the rear wall 172 have beeninterconnected by means of a substantially rectangular vertical firstside wall 175 and second side wall 176. The walls 171,172, 173,174,175,176 define a hollow cavity space 190 in their interior, in whichspace the disk 180 attached to the axle journal 12 revolves along withthe axle journal 12. The axle journal 12 extends through the hole 177provided in the front wall 171 of the fastening flange construction 170and through the hole 178 provided in the rear wall 172 and has beenmounted revolvingly by means of a bearing 15 in the rear wall 172. Thediameter of the hole provided in the front wall is larger than the outerdiameter of the axle journal 12.

Further in the embodiment shown in FIG.1, on the outer circumference ofthe disk 180 on its opposite side faces 180 a, 180 b, hydraulic loadingelements 190,191 have been fitted, by whose means the disk 180 and,thereby, the axle journal 12 can be bent. The pistons 190 a, 191 a ofthe loading elements 190,191 move in cylinders 200, 201 which have beenformed into the front wall 171 and the rear wall 172 of the fasteningflange construction 170. To the bottoms of the cylinders 200,201,pressure medium ducts 210,211 pass. The pistons 190 a, 191 a have beensealed in the cylinders 200,201 by means of sealing members known inthemselves, which members are not shown in the figure. Also, thincapillary ducts (not shown in the figure) pass through the pistons 190a,191 a into lubrication pockets 220,221 of the loading elements190,191. There are favourably four loading elements 190,191 on each face180 a,180 b of the disk 180, i.e. a total of eight elements. The loadingelements 190, 191 are placed at the intersection points between thecircumference of a circle drawn at the centre of the axle journal 12,the X-axis, and the Y-axis.

In the embodiment as shown in FIG. 14, the axle journal 12 and, thereby,the roll mantle 11 are bent by means of the disk 180 attached to theaxle journal 12 and by means of the hydraulic loading elements 190,191acting upon said disk. By means of eight loading elements 190, 191, theroll mantle 11 can be bent to the desired curve form and to the desiredangular position.

FIG. 15 shows an embodiment which differs from the embodiments shown inthe preceding figures in respect of the bending mechanism, thebearing-arrangement, and the axle journal. In this embodiment, the axlejournal 12 is of substantially uniform thickness over its entire length,and it is not bent. The journalling of the axle journal 12 in a firstsupport sleeve 13 fitted inside the roll mantle 11 has been arranged bymeans of hydrostatic or hydrodynamic glide bearings 70,71, on whosesupport the roll mantle 11 revolves in relation to the axle journals 12.The glide bearings 70,71 are placed at a distance from one another inthe direction of the axis X—X of the roll. For the feed and return ductsof the hydraulic medium, a duct 72 parallel to the axis X—X of the axlejournal has been made into the axle journal 12, together with radialducts 73,74 at the locations of the glide bearings. The first bearing70, which operates exclusively as a glide bearing, has been attached tothe axle journal 12 by means of an articulated joint so that its centralaxis Y—Y can turn in relation to the radius of the axle journal 12.

In the embodiment shown in FIG. 15, in addition to the glide bearingproperty, the second bearing 71 has been provided with a possibility todisplace the bearing in the direction of the radius of the axle journal12. This second bearing 71 has been attached to the axle journal 12 sothat it can move in the direction of the radius of the axle journal 12,and at the same time its central axis Y—Y can turn in relation to theradius of the axle journal 12. Into this second bearing 71, twoseparately controllable hydraulic feeds 74 a,74 b are passed. By meansof this arrangement, it is possible to control the movement of thebearing 71 in relation to the radius of the axle journal 12. When thebearing 71 is shifted in relation to the radius of the axle journal 12,this produces a bending force applied to the roll mantle 11.

The alternative embodiment shown in FIG. 3, in which the bending device30 is placed between the roll and the nearest fastening member 18, can,of course, also be applied to the embodiments shown in FIGS. 4 through9.

In FIGS. 10 through 13, it is shown that the bending is carried out atthe second, outer support point, in relation to the end 52 of the roll,but a reversed situation is also possible. In such a case, the bendingmechanism is placed at the inner support point, and the outer supportpoint is fixed.

In the embodiments shown in FIGS. 2 through 5, 7, 8, 10 and 13, thebending of the roll mantle 11 takes place by means of forced shifting bymeans of a screw 30,80, a screw-nut assembly 120,130,151 . . . 153, awedge 70, or equivalent. The screw 30, 80, the screw-nut assembly120,130,151 . . . 153, the wedge 70, or equivalent binds the axlejournal 12 with the support point rigidly, in which case the roll is, soto say, rigidly supported in the sense of vibration.

In the embodiments shown in, FIGS. 6, 9, 11, 12, and 14, the bending ofthe roll mantle 11 takes place by means of hydraulics, pneumatics, or bymeans of a stepping motor 100,101,190,250,260 in which case the roll is,so to say, freely supported or articulation-supported in the sense ofvibration. A hydraulic medium and a pneumatic medium usually yield tosome extent, in which case the support is provided with a slight extentof resilience.

In the embodiment shown in FIG. 15, the bending of the roll mantle 11takes place directly from the roll mantle 11 from inside the supportpoint of the axle journal 12. In this case the bearings 70,71 bind theroll with the first support sleeve 13 rigidly. Thus, also in thisembodiment, the roll is rigidly supported in the sense of vibration.

In the case of rigid support, the lowest natural frequency of the rollbecomes more than twice as high as compared with a freely supportedroll. When the natural frequency of a roll becomes higher, it ispossible to use smaller roll diameters, in which case the forcestransferred from the bending to the frame of the machine are reduced andthe cost of manufacture of the roll becomes lower.

In the following, the patent claims will he given, and the details ofthe invention may show variation within the scope of the inventive ideadefined in said claims and differ from what has been stated above by wayof example only.

What is claimed is:
 1. A roll that can be bent for a web-like materialhaving an axis (X—X), and a continuous tubular roll mantle (11) of acomposite material having two opposite end portions, each end portioncomprising: an axle journal (12) having an inner part extending withinthe end portion of the roll mantle and an outer part protruding out fromthe end portion of the roll mantle, said inner part being attached tothe respective end portion of the roll mantle (11); an articulationmember (16) provided on an outer face of the outer part of the axlejournal (12); a first support sleeve (13) extending within the endportion of the roll mantle and having an inner surface and an outersurface, said first support sleeve being fixed in the interior of therespective end portion of the roll mantle (11); first and secondfastening means (18,19) placed at a distance from one another in thedirection of the axis (X—X) of the roll, said fastening means beingfixed to a frame (R) of a machine incorporating the roll; bearings(14,15) having inner races and outer races, the roll mantle (11) beingjournalled revolving by means of said bearings (14,15) placed at adistance from one another in the direction of the axis (X—X) of theroll, the outer races of said bearings (14,15) being supported on saidfirst support sleeve (13) and the inner races of said bearings (14,15)being supported on the axle journal (12); a second support sleeve (17)having an inner surface and an outer surface, said second support sleeve(17) surrounding the outer end of the axle journal (12) and extending ina direction of the axis (X—X) of the roll at least between saidfastening means (18,19), the outer end of the axle journal (12) restingby means of the articulation member (16) against the inner surface ofthe second support sleeve (17) and the outer surface of the secondsupport sleeve (17) being fixed in the fastening means (18,19); and abending mechanism (30,70,100) arranged between the second support sleeve(17) and the axle journal (12) in order to displace the axle journal(12) in relation to the second support sleeve in a direction transverseto the direction of the axis (X—X) of the roll and thereby bend the rollmantle (11) into an arc form (FIGS. 2-6).
 2. A roll as claimed in claim1, wherein the articulation member (16) of the axle journal (12) isplaced substantially at the first fastening means (18), the axle journal(12) being diverted by means of a bending mechanism (30,70,100) fittedsubstantially at or near the second fastening means (19) (FIGS. 2 and4-6).
 3. A roll as claimed in claim 2, wherein the bending mechanismcomprises a screw member (30), being passed through the second supportsleeve (17) and through the axle journal (112), said screw member (30)being locked against movement taking place in a direction of alongitudinal axis of the screw member (30) by means of fastening members(31, 32) supported against the outer surface of the second supportsleeve (17) and attached to the screw member (30), said screw member(30) being provided with an outside threading substantially over theportion that extends through the second support sleeve (17), the borereceiving the screw member (30) in the axle journal (12) being providedwith a corresponding inside threading, wherein the screw member (30)produces a torque which bends the axle journal (12), which torque againbends the roll mantle (11) (FIGS. 24).
 4. A roll as claimed in claim 2,wherein the bending mechanism comprises a screw member (60) beingprovided with an outside threading, said screw member (60) being movablein the direction of the axis (X—X) of the roll, and being fitted in afastening member (61) attached to the inner surface of the secondsupport sleeve (17) and provided with a bore which is parallel to theaxis (X—X) of the roll, said fastening member (61) being provided withan inside threading that receives the screw member (60), an end of thescrew member (60) being placed against an end face of a first wedgemember (70), said first wedge member (70) being movable along the innersurface of the second support sleeve (17) in a direction parallel to theaxis (X—X) of the roll, but which first wedge member is locked againstthe inner surface of the second support sleeve (17) to prevent radialmovement, a wedge face of said first wedge member (70) being supportedagainst a wedge face of a second wedge member (71) attached to the axlejournal (12), wherein pushing of the first wedge member (70) onto thesecond wedge member (71), with the screw member (60), produces a forcethat bends the axle journal (12), which force again bends the rollmantle (11) (FIG. 5).
 5. A roll as claimed in claim 2, wherein thebending mechanism comprises a hydraulic cylinder, pneumatic cylinder orstepping motor (100) attached to the second support sleeve (17), a rod(101) of said cylinder or motor being attached to the axle journal (12),wherein movement of the rod (101) produces a force that bends the axlejournal (12), which force again bends the roll mantle (11) (FIG. 6). 6.A roll as claimed in claim 1, wherein the articulation member (16) ofthe axle journal (12) is placed substantially at the location of thesecond fastening means (19), the axle journal (12) being diverted bymeans of a bending mechanism (30,70,100) fitted substantially at or nearthe location of the first fastening means (18) (FIG. 3).
 7. A roll asclaimed in claim 1, wherein the first (18) and second (19) support meansare attached to a common lower part (90), said common lower part (90)being attached to the framed (R) of the machine incorporating the roll(FIG. 4).
 8. A roll as claimed in claim 1, wherein a regulation device(40) is fitted onto the second fastening member (19), said regulatingdevice (40) acting upon a bearing member (21) supported against theouter surface of the second support sleeve (17,51) by an intermediate ofan intermediate member (22), wherein a movement of rotation of theregulation device (40) in a direction of a circumference of the rollproduces a corresponding movement of rotation in the second supportsleeve (17) and from it further, by an intermediate of the bendingmechanism (30,60,80,100), in the axis journal (12) in order to controlthe radial direction of the bending arc of the roll mantle (11) (FIGS.2-9).
 9. A roll that can be bent for a web-like material having an axis(X—X), and a continuous tubular roll mantle (11) of a composite materialhaving two opposite end portions, each end portion comprising: an axlejournal (12) having an outer face and being attached directly by meansof an end member (52) to the respective end portion of the roll mantle(11); first and second fastening means (18,19) placed at a distance fromone another in the direction of the axis (X—X) of the roll, saidfastening means being fixed to a frame (R) of a machine incorporatingthe roll; a first support sleeve (50) having an inner surface and anouter surface, said first support sleeve (50) surrounding the axlejournal (12) and extending in the direction of the axis (X—X) of theroll from the first fastening means (18) to a distance outside thesecond fastening means (19), said extension beyond the second fasteningmeans (19) forming an outer portion of the first support sleeve (50);bearings (14,15) having inner races and outer races and being fittedsubstantially at a location of the fastening means (18,19), said axlejournal (12) being journalled revolving by means of said bearings(14,15), the outer races of said bearings being supported on said firstsupport sleeve (50) and the inner races of said bearings being supportedon the axle journal (12); a second support sleeve (51) having an innersurface and an outer surface, said second support sleeve (51)surrounding the first support sleeve (50) and having a thicker portion(51 a) placed at the location of the first fastening means (18) anddirected at the axle journal (12), which thicker portion (51 a) forms anarticulation member of the first support sleeve (50), said secondsupport sleeve (51) extending in the direction of the axis (X—X) of theroll from the first fastening means (18) to a distance outside thesecond fastening means (19) and the outer surface of said second supportsleeve (51) being fixed in the fastening means (18,19), said extensionbeyond the second fastening means (19) forming an outer portion of thesecond support sleeve (51); and a bending mechanism (60,70,80,100)arranged between the second support sleeve (51) and the first supportsleeve (50) in order to displace the first support sleeve (50) inrelation to the second support sleeve and thereby the axle journal (12)in a direction transverse to the direction of the axis (X—X) of the rolland thereby bend the roll mantle (11) into an arc form (FIGS. 7-9). 10.A roll as claimed in claim 9, wherein a screw member (80) being providedwith an outside treading and having a longitudinal axes is fitted on theouter portions of the first and the second support sleeve (50,51), saidscrew member (80) passing through the first and the second supportsleeves (50,51), movement of said screw member (80) in the direction ofthe longitudinal axis in relation to the first support sleeve (50) beingprevented by means of first fastening members (81,82) attached to thescrew member (80) and supported against the inner surface of the firstsupport sleeve (50), said screw member (80) being connected with secondfastening members (83,84) attached to the outer surface of the secondsupport sleeve (51) and provided with bores having an inner threadingreceiving the outside threading on the screw member (80), said screwmember (80) producing a torque which bends the first support sleeve (50)and thereby the axle journal (12), and which torque also bends the rollmantle (11) (FIG. 7).
 11. A roll as claimed in claim 9, wherein a screwmember (60) being provided with an outside treading is fitted to theouter portion of the second support sleeve (51), said screw member (60)being movable parallel to the axis (X—X) of the roll, and being fittedin a fastening member (61) attached to the inner surface of the secondsupport sleeve (51) and provided with a bore parallel to the axis (X—X)of the roll having an inside threading receiving the screw member (60),wherein an end of the screw member (60) directed at the end portion ofthe roll mantle (11) is positioned against an end face of a first wedgemember (70), said wedge member (70) being movable along an inner surfaceof the second support sleeve (51) in a direction parallel to the axis(X—X) of the roll, said first wedge member (70) being locked against theinner surface of the second support sleeve (51) to prevent radialmovement, a wedge face of said first wedge member (70) being supportedagainst a wedge face of a second wedge member (71) attached to the outersurface of the first support sleeve (50), said first wedge member (70)being pushed onto the second wedge member (71) with the screw member(60) produces a torque that bends the first support sleeve (50) andthereby the axle journal (12), which torque again bends the roll mantle(11) (FIG. 8).
 12. A roll as claimed in claim 9, wherein a hydrauliccylinder, pneumatic cylinder or stepping motor (100) is fitted onto theouter portions of the first and the second support sleeve (50,51), saidcylinder or motor being attached to the second support sleeve (51), saidcylinder or motor having a rod (101) being attached to the first supportsleeve (50), wherein movement of the rod (101) produces a torque, whichbends the first support sleeve (50) and thereby the axle journal (12),and which torque also bends the roll mantle (11) (FIG. 9).
 13. A rollthat can be bent for a web-like material having an axis (X—X), and acontinuous tubular roll mantle (11) of a composite material having twoopposite end portions, each end portion comprising: an axle journal (12)having an outer face and being attached directly by means of an endmember (52) to the respective end portion of the roll mantle (11); firstand second fastening means (18, 110) placed at a distance from oneanother in the direction of the axis (X—X) of the roll, said fasteningmeans being fixed to a frame (R) of a machine incorporating the roll andsaid second fastening means (110) being L-shaped; bearings (14,15)having inner races and outer races, said axle journal (12) beingjournalled revolving by means of said bearings (14,15), the outer raceof a first bearing being supported on the first fastening means (18) andthe outer race of a second bearing being supported on the secondfastening means (110), the inner races of the first (14) and second (15)bearings being supported on the axle journal (12); a bending mechanism(120, 130) being arranged between the second fastening means (110) andthe axle journal (12) in order to displace the axle journal (12) inrelation to the second fastening means in a direction transverse to thedirection of the axis (X—X) of the roll and thereby bend the roll mantle(11) into an arc form; and wherein the bending mechanism comprises,substantially in a vertical plane (Y), a first regulation mechanism(120) fitted between a horizontal part of the L-shaped second fasteningmeans (110) and a flange (113) that surrounds the second bearing (15)and, substantially in a horizontal plane (X), a second regulationmechanism (130) fitted between a vertical part of the L-shaped secondfastening means (110) and the flange (113) that surrounds the secondbearing (15) (FIG. 10).
 14. A roll as claimed in claim 13, wherein thefirst (120) and the second (130) regulation mechanism comprise a firstpin (121,131) being attached to the flange (113) and provided with anoutside threading, and a second, opposite pin (122,132) being attachedto a sledge (124,134) moving on the fastening member (110) and beingprovided with an outside threading, said opposite pins (121,122,131,132)being interconnected by means of a nut member (123,133) provided with aninside threading, by means of which nut member (123,133) the curve formof the roll mantle (11) and the angular position of the curve form ofthe roll mantle (11) is regulated (FIG. 10).
 15. A roll that can be bentfor a web-like material having an axis (X—X), and a continuous tubularroll mantle (11) of a composite material having two opposite endportions, each end portion comprising: an axle journal (12) having anouter face and being attached directly by means of an end member (52) tothe respective end portion of the roll mantle (11); first and secondfastening means (18, 19) placed at a distance from one another in thedirection of the axis (X—X) of the roll, said fastening means beingfixed to a frame (R) of a machine incorporating the roll; bearings(14,15) having inner races and outer races, said axle journal (12) beingjournalled revolving by means of said bearings (14,15), the outer raceof a first bearing being supported on the first fastening means (18) andthe outer race of a second bearing being supported on the secondfastening means (19,19 a,113), the inner races of first (14) and second(15) bearings being supported on the axle journal (12); a bendingmechanism (250) being arranged between the second fastening means (19)and the axle journal (12) in order to displace the axle journal (12) inrelation to the second fastening means in a direction transverse to thedirection of the axis (X—X) of the roll and thereby bend the roll mantle(11) into an arc form; and wherein at least the second bearing (15) is amagnetic bearing (250), by whose means the curve form of the roll mantle(11) and the angular position of the curve form of the roll mantle (11)is regulated (FIG. 11).
 16. A roll that can be bent for a web-likematerial having an axis (X—X), and a continuous tubular roll mantle (11)of a composite material having two opposite end portions, each endportion comprising: an axle journal (12) having an outer face and beingattached directly by means of an end member (52) to the respective endportion of the roll mantle (11); first and second fastening means (18,19 b) placed at a distance from one another in the direction of the axis(X—X) of the roll, said fastening means being fixed to a frame (R) of amachine incorporating the roll; bearings (14,15) having inner races andouter races, said axle journal (12) being journalled revolving by meansof said bearings (14,15), the outer race of a first bearing beingsupported on the first fastening means (18) and the outer race of asecond bearing being supported on the second fastening means (19,19a,113), the inner races of first (14) and second (15) bearings beingsupported on the axle journal (12); a bending mechanism (260) beingarranged between the second fastening means (19 b) and the axle journal(12) in order to displace the axle journal (12) in a directiontransverse to the direction of the axis (X—X) of the roll and therebybend the roll mantle (11) into an arc form; and wherein a flange (19 a)that surrounds the second bearing (15) the second fastening means (19 b)communicate with each other by means of a magnet (260), by whose meansthe curve form of the roll mantle (11) and the angular position of thecurve form of the roll mantle (11) is regulated (FIG. 12).
 17. A rollthat can be bent for a web-like material having an axis (X—X), and acontinuous tubular roll mantle (11) of a composite material having twoopposite end portions, each end portion comprising: an axle journal (12)having an outer face and being attached directly by means of an endmember (52) to each end portion of the roll mantle (11); first andsecond fastening means (18, 140) placed at a distance from one anotherin the direction of the axis (X—X) of the roll, said fastening meansbeing fixed to a frame (R) of a machine incorporating the roll; bearings(14,15) having inner races and outer races, said axle journal (12) beingjournalled revolving by means of said bearings (14,15), the outer raceof a first bearing being supported on the first fastening means (18) andthe outer race of a second bearing being supported on the secondfastening means (140), the inner races of first (14) and second (15)bearings being supported on the axle journal (12); a bending mechanism(153) being arranged between the second fastening means (140) and theaxle journal (12) in order to displace the axle journal (12) in relationto the second fastening means in a direction transverse to the directionof the axis (X—X) of the roll and thereby bend the roll mantle (11) intoan arc form; and wherein a first pin (151) provided with an outsidethreading is attached to a fastening flange (113) of the second bearing(15), and a second, opposite pin (152) provided with an outsidethreading is attached to a gearwheel device (150) moving on the secondfastening means (140), said opposite pins (151,152) being interconnectedby means of a nut member (153) provided with an inside threading, agearwheel (154) of a gearwheel device (150) is movable along a rack(161), shaped as an arc of a circle, of a rack device (160) attached tothe second fastening means (140), the curve form of the roll mantle (11)being regulated by means of the nut member (153), and the angularposition of the curve form of the roll mantle (11) being regulated bymeans of the gearwheel-rack device (150,160) (FIG. 13).
 18. A roll thatcan be bent for a web-like material having an axis (X—X), and acontinuous tubular roll mantle (11) of a composite material having twoopposite end portions, each end portion comprising: an axle journal (12)having an outer face and being attached directly by means of an endmember (52) to each end portion of the roll mantle (11); a fasteningflange construction (170) being attached to a frame (R) of a machineincorporating the roll, said flange construction comprising twosubstantially rectangular vertical walls, a front wall (171) and a rearwall (172), placed at a distance from one another in a direction of theaxis (X—X) of the roll, a bottom edge and a top edge of said walls(171,172) being interconnected by means of substantially rectangularhorizontal walls, a bottom wall (173) and a top wall (174), said walls(171,172) having side edges being interconnected by means ofsubstantially rectangular vertical walls, a first side wall (175) and asecond side wall (176), the walls (171,172,173,174,175,176) defining ahollow cavity space (190), in which a disk (180) attached to the axlejournal (12) revolves along with the axle journal (12), which axlejournal (12) extends through a hole (177) provided in the front wall(171) of the fastening flange construction (170) and through a hole(178) provided in the rear wall (172) and is journalled revolving bymeans of a bearing (15) in the rear wall (172); and wherein saidfastening flange construction (170) further comprises loading elements(190,191) acting upon opposite faces (180 a,180 b) of the disk (180), bymeans of which loading elements the disk (180) and, thereby, the axlejournal (12) and, thereby further, the roll mantle (11) is bent into acurve form, and the angular position of the arc of the roll mantle (11)is regulated (FIG. 14).
 19. A roll that can be bent for a web-likematerial having an axis (X—X), and a continuous tubular roll mantle (11)of a composite material having two opposite end portions, each endportion comprising: an axle journal (12) having an inner part extendingwithin the end portion of the roll mantle and an outer part protrudingout from the end portion of the roll mantle, said inner part beingattached to the respective end portion of the roll mantle (11); firstand second fastening means (18,19) placed at a distance from one anotherin the direction of the axis (X—X) of the roll, said fastening meansbeing fixed to a frame (R) of a machine incorporating the roll, theouter part of said axle journal (12) being supported by said first andsaid second fastening means (18,19); a support sleeve (13) having aninner surface and an outer surface and being fitted in the interior ofeach end portion of the roll mantle (11); and hydrostatic orhydrodynamic glide bearings (70,71) having a central axis (Y—Y) andbeing arranged between the inner part of the axle journal (12) and thesupport sleeve (13) and supporting the axle journal (12) to the supportsleeve (13), said roll mantle (11) being journalled revolving by meansof said glide bearings (70,71) on the axle journal (12), said bearings(70,71) also forming a bending mechanism by which the roll mantle (11)is bent into a curve form, said glide bearings (70,71) acting upon thesupport sleeve (13) supported against the axle journal (12), which glidebearings (70,71) have been attached to the axle journal (12) so that thecentral axes (Y—Y) of the glide bearings (70,71) are rotatable inrelation to a radial direction of the axle journal (FIG. 15).
 20. A rollas claimed in claim 19, wherein into one of the hydraulic glide hearings(71), hydraulic medium is supplied by means of two separatelycontrollable feeds (74 a,74 b), wherein one of the hydraulic glidebearings (71) is displaced in the direction of a radius of the axis ofthe roll so that the central axis (Y—Y) of the glide bearing (71) formsan angle in relation to the radial direction of the axis of the roll, asa result of which the roll mantle (11) bends (FIG. 15).
 21. A roll asclaimed in claim 20, wherein the second fastening member (19) isprovided with a regulation device (40), which acts upon a bearing member(21) supported against the outer face of the axle journal (12) by anintermediate of an intermediate member (22), wherein a movement ofrotation of the regulation device (40) in the direction of acircumference of the roll produces a corresponding movement of rotationin the axle journal (12) in order to control the radial direction of thebending arc of the roll mantle (11) (FIG. 15).